Nut-cracking machine

ABSTRACT

A machine for cracking the shells of walnuts and the like so as to enable separation from the shell of the nut kernel otherwise confined therewithin. The machine includes a container defining a compartment or reservoir for the receipt of nuts therewithin, conveyor means passing through such compartment for removing nuts one-by-one therefrom and for advancing the same in spaced apart succession into a cracking station, and nut-cracking means at such station and including both anvil structure and hammer structure aligned therewith. The hammer structure comprises gripper mechanism for displacing a hammer element into engagement with a nut to hold the same, in cooperation with the anvil structure, at a predetermined location, and it further comprises force applicator mechanism for imparting a displacement force of predetermined magnitude to such hammer element to cause the same to crack the shell of a nut then constrained against movement by the cooperative anvil structure.

United States Patent John J. Lindsey Lafayette, Calif. (2608 Janna Ave. Modesto, Calif. 95350) [2 l Appl. No. 733,598

[22] Filed May 31, 1968 [45] Patented Feb. 9, 1971 [72] Inventor [54] NUT-CRACKING MACHINE 6 Claims, 11 Drawing Figs.

Primary Examiner-Willie G. Abercrombie Attorney-Gardner & Zimmerman ABSTRACT: A machine for cracking the shells of walnuts and the like so as to enable separation from the shell of the nut kernel otherwise confined therewithin. The machine includes a container defining a compartment or reservoir for the receipt of nuts therewithin, conveyor means passing through such compartment for removing nuts one-by-one therefrom and for advancing the same in spaced apart succession into a cracking station, and nut-cracking means at such station and including both anvil structure and hammer structure aligned therewith. The hammer structure comprises gripper mechanism for displacing a hammer element into engagement with a nut to hold the same, in cooperation with the anvil structure, at a predetermined location, and it further comprises force applicator mechanism for imparting a displacement force of predetermined magnitude to such hammer element to cause the same to crack the shell of a nut then constrained against movement by the cooperative anvil structure.

PATENTEI] FEB 9m:

sumama INVENTOR. John J. Lindseq 135 Attorne PATENTEUFEB 9m SHEET 3 OF 3 INVENTOR. John J. Lindsey Attorneys NUT-CRACKING MACHINE This invention relates to a machine for cracking the shells of walnuts and the like, and it relates more particularly to a machine for removing nuts one-by-one in spaced apart succession from a container therefor and for then advancing such nuts, several at a time, in step-by-step progression into a cracking station at which the shells of the nuts are broken so as to release the kernels therefrom.

After being harvested and the outer husks removed therefrom, substantially all nuts comprise a hard shell that encapsulates a kernel or nut meat therewithin constituting the edible portion of the nut. Accordingly, it is necessary to crack such hard shell in order to provide access to the usable kernel contained therewithin, and with English walnuts and similar nuts cracking the shells thereof usually releases the kernel therefrom. Evidently, then, in commercial environments it is both feasible and usually desirable to crack the shells of such nuts with automatic machinery so as to increase the rate of production of the edible nut kernel and to reduce costs by minimizing the requirement for manual processing.

In view thereof, the present invention has for an object, among others, to provide an improved machine for cracking the shells of nuts and the like so as to permit separation from the shells of the edible kernels otherwise confined therewithin. The apparatus for accomplishing such object includes a hopper or container defining a reservoir adapted to receive a supply of nuts, and it further includes conveyor apparatus having an elevator section that passes through such container and is equipped with a plurality of spaced apart flights adapted to remove nuts one-by-one from the container and to then ad vance the same in single-file, step'by-step succession into a cracking station, several nuts at a time. When in the cracking station, the nuts are first gripped and held between anvil structure and hammer structure and are then cracked by displacement of a hammer element through a predetermined distance toward the anvil structure which is immovable at such time. The conveyor apparatus then removes such cracked nuts from the cracking station and, contemporaneously therewith, advances another plurality or grouper nuts into the station.

Additional objects and advantages of the invention, especially as concerns particular features and characteristics thereof, will become apparent as the invention is explained with reference to the specific embodiment thereof illustrated in the accompanying drawings in which:

FIG. 1 is a side view in elevation of a nut cracking machine embodying the invention;

FIG. 2 is an enlarged, broken side view in elevation illustrating the opposite side of the machine as it is shown in FIG. 1;

FIG. 3 is a broken end view in elevation taken generally along the line 3-3 of FIG. 1;

FIG. 4 is a broken top plan view of the machine as illustrated in FIG. 2, portions of the structure being broken away to show certain of the internal gear trains;

FIG. 5 is a further enlarged, side view in elevation of the conveyor structure showing in phantom form a nut supported within a pocket defined between successive flights of the conveyor apparatus;

FIG. 6 is a broken top plan view of one of the pocket-forming rollers of the conveyor apparatus shown in FIG. 5;

FIG. 7 is a broken transverse sectional view taken generally along the line 7-7 of FIG. 4;

FIG. 8 is a vertical sectional view taken generally along the line 8-8 of FIG. 7;

FIG. 9 is a transverse sectional view taken generally along the line 9-9 of FIG. 4;

FIG. 10 is an enlarged, fragmentary view illustrating the details of one of the anvil structures; and

FIG. 11 is an enlarged, broken sectional view taken along the line 1141 of FIG. 3. r

The illustrative embodiment of the nut cracking machine shown in the drawings includes frame structure 15 that comprises a plurality of upwardly extending frame elements or legs 16 (there being four in number), longitudinally extending frame elements 17, and transversely'extending frame elements I8. The frame elements are all fixedly secured to each other by welding or other conventional means, and the frame structure may be reinforced wherever necessary to rigidify the same, as by means of gussets 19 as shown in FIG. 1. The longitudinally extending frame elements 17 project beyond the legs I6 at one end of the machine, and are equipped adjacent their outer ends with vertically oriented support structure 20 onto which is affixed a hopper or container 21 defining a compartment or reservoir 22 adapted to receive a plurality of nuts 23 therewithin. The container 21 has: a downwardly and inwardly inclined sidewall and is generally a half section of a right cone (or frustum thereof) that is inverted so that the apex or smallest portion thereof is at the bottom. Thus, the mass of nuts 23 within the compartment 22 are forced downwardly and inwardly toward the support structure 20.

The machine is provided with conveyor apparatus, generally denoted with the numeral 24, which has an elevator section 25 passing upwardly through the container 21 along the support structure 20. As shown best in FIGS. 3 and 4, the conveyor apparatus 24 includes a pair of transversely spaced endless chains 26a and 26b respectively entrained about a plurality of sprockets which, considering the chain 26a, are respectively denoted with the numerals 27a, 28a and 29a (it being appreciated that there are three additional sprockets arranged with the chain 2611 and disposed in paired relationship with the respectively corresponding sprockets 27a, 28a and 29a). The chains 26a and 26b are essentially conventional link chains, as is apparent in FIG. 6, and they are interconnected by a plurality of transversely disposed rollers 30 extending therebetween which are secured to each of the chains 26 at longitudinally spaced intervals such that certain of the adjacent rollers 30 define pockets 3] therebetween which are adapted to respectively seat therein one of the nuts 23 removed by the conveyor apparatus from the container 21.

Referring to FIG. 6, it will be observed that each of the rollers 30 is rotatably relates to the chains 26 and comprises an elongated pin 32 that extends between the chains 26 and through certain of the links thereof. Rotatably mounted upon the pin 32 is a spool 33 having outwardly extending flanges 34 at each end thereof spaced inwardly slightly from thechains 26. An outer sleeve 35 is coaxially circumjacent the spool 33 and has end portions crimped inwardly about the flanges 34, as shown at 36, so as to fixedly secure the sleeve to the spool. The outer surface of the sleeve 35 may be serrated or otherwise roughened, as illustrated, so as to provide a good frictional engagement with the outer surface of the shell of a nut 23, as shown in FIG. 5.

The conveyor 24 is also provided at spaced apart intervals therealong with a plurality of flights or elevator components 37, each of which (as shown in FIGS. 3 and S) is provided along one surface thereof with a concave or dish-shaped receptacle 38 adapted to seat a nut 23 therein, as shown in FIG. 1, so as to carry such nut upwardly from the container 21 as the flights move upwardly therethrough. The flights 37 project outwardly from the conveyor 24, as is most apparent in FIG. 1, and are secured to each of the chains 26 in any suitable manner as, for example, by being rivetedl or otherwise secured at each end thereof to the inwardly turned ear 39 of a link 40 forming a part of the chain, as shown in FIGS. 5 and 6. Thus, the flights 37 are maintained in a predetermined orientation with respect to the endless chains 26 and always project outwardly therefrom, but because of the pivotal connection of the links 40 with the chains, the slight articulations necessary to enable the endless chains to traverse the arcuate paths defined by the sprockets 27, 28 and 29 are afforded. As is most apparent in FIG. 2, the flights 37 are spaced apart by two rollers 30 interposed therebetween so that a pocket 31 is defined between any two successive flights.

In order to prevent sagging of the conveyor apparatus as it advances nuts into and through the cracking station generally denoted 41 in the drawings, a longitudinally extending bar 42 (FIG. 7) is provided in underlying relation with the upper leg or reach of the conveyor, and such support is adapted to be rollingly engaged by the rollers 30. The support bar 42 maintains the rollers 30 at a predetermined elevation as they pass through the cracking station 41, and it also imparts a rotational motion to the rollers which is effective to properly position the nuts 23 within the pockets 31 for cooperative engagement with the hammer and anvil structures to be described hereinafter. The upper surface of the bar 42 is coated with rubber or other material have a high coefficient of friction to facilitate imparting such rotational motion to the rollers 30.

The bar 42 is supported at longitudinally spaced locations by spring structures 43, as shown in FIGS. 1 and 2, which resiliently bias the support bar upwardly but accommodate any slight downward displacements which may be enforced thereon. Each spring structure comprises a hollow sleeve or post 44 fixedly secured to the frame structure of the apparatus, a rod slidably mounted within the post 44 and equipped at its upper end with a clevis 45 secured to the bar 42, and a helical compression spring 46 seated at one end within the post 44 and bearing upwardly at its other end against the clevis 45 so as to resiliently urge the bar 42 upwardly.

The conveyor apparatus 24 is driven by an electric motor 47 coupled by an endless belt 48 to a drive sheave 49 constrained upon a shaft 50 so as to rotatably drive the same. The shaft 50, as shown best in FIG. 4, extends transversely of the machine and is joumaled for rotation at spaced apart locations therealong. Adjacent one side of the machine, the shaft 50 is equipped with a gear 51 that drivingly engages a gear 52 of greater diameter that is pinned or otherwise secured to a shaft 53 so as to rotatably drive the same. The shaft 53 is joumaled for rotation and extends outwardly at one side of the machine and is equipped thereat with a crank wheel or is equipped thereat with a crank wheel or disc 54. Pivotally secured to the disc 54 a spaced distance from the axis of rotation thereof is a crank arm 55 having one end of a drive shaft or push rod 56 secured thereto.

The rod 56, as shown in FIG. 2, may be provided with turn buckle or other conventional means to adjust the length thereof, and at its opposite end it is pivotally secured to a crank arm 57 cooperative with a rotatable disc or wheel 58 to impart unidirectional angular displacements thereto. The disc 58 is equipped with an elongated collar 59 (FIG. 3) that is splined or keyed or otherwise constrained upon a shaft or rod 60 extending completely therethrough. At the outer end of such shaft, the hub 57a of the arm 57 is pivotally supported thereon, and the arm is connected by a ratchet or one-way clutch arrangement with the disc 58 so as to drive the same intermittently in one angular direction as the arm 57 is cyclically reciprocated in opposite angular directions, as indicated by the arrows in FIG. 2, between the two positions respectively shown by full and broken lines.

In this respect, the disc 58 is provided at 90 intervals along the circumferential surface thereof with stepped notches or recesses 590 (FIG. 11) each having a radially oriented surface or shoulder adapted to have seated thereagainst a spring loaded rivet pin or lug 60a pivotally carried by the arm 57. As the arm is angularly displaced in a clockwise direction, as viewed in FIG. 2 (counterclockwise as seen in FIG. 11), the lug 60a rides out of the open end of the recess 59a then containing the same, slides along the edges of the disc 58, and then snaps into the next successive recess 590 at the time that the arm 57 has been displaced through a distance of about 90. When the arm 57 is angularly displaced in the opposite direction, the pin 60a engages the closed end of the recess in which it is then seated and is effective to carry the disc 58 with it.

The shaft 60 is equipped at its inner end with a drive gear 61 that meshingly engages a gear 62 of reduced diameter that drives a shaft 63 upon which the sprockets 29 are mounted. A friction brake 64 engages the collar 59 and imparts a frictional inhibition to free angular displacements thereof, which is effective to prevent overtravel of the conveyor structure, as will be described hereinafter. The amount of frictional resistance imparted to the collar 59 may be selectively determined by adjustment of a nut and elongated bolt device 65 forming a part of the friction brake assembly.

Evidently, then, the sprockets 29 are drive sprockets that impart motion to the conveyor apparatus 24, and the sprockets 27 and 28 are idlers that determine the configuration of the conveyor and, in particular, define the extent of the elevator section 25 thereof. Whenever the motor 47 is energized through conventional switch and control circuitry (not shown), the drive sheave 49, shaft 50, and shaft 53 and crank disc 54 drivingly connected thereto are all continuously driven. However, the motion imparted to the conveyor apparatus 24 is intermittent because of the action of the one-way drive defined between the crank arm 57 and disc 58, as explained heretofore.

Thus, as the disc 54 rotates continuously and therefore causes the crank arm 55 to continuously traverse a circular path of travel described about the axis of rotation of the disc 54, the push rod 56 is reciprocated generally along the longitudinal axis thereof between the one extreme position thereof shown in FIG. 2 in which the arm 57 assumes the location shown by full lines, and its alternate extreme position in which the crank ann 55 has been angularly displaced by 180 by and the arm 57 has been displaced into the position shown by broken lines. As the arm 57 cyclically reciprocates in opposite directions through an angular distance approximating 90, the one-way drive causes the shaft 60 and gear 61 to be displaced only in a counterclockwise direction (as viewed in FIG. 2), with the result that the gear 62 and drive sprockets 29 are rotated intermittently in a clockwise direction, as observed in FIG. 2 and as indicated by the arrow associated with the conveyor apparatus 24. Evidently, the distance through which the conveyor apparatus is displaced is the linear equivalent of the 90 angular distance through which the sprockets 29 are displaced upon each movement of the crank arm 55 through an angular distance of into the full-line position thereof shown in FIG. 2.

Referring to FIG. 4, it may be observed that the distance through which the conveyor apparatus 24 is displaced each time it is intermittently energized is substantially equal to the longitudinal length of the cracking station 41 and, in more specific terms, is substantially equal to the length of the conveyor required to hold four successive nuts 23, since four nuts are cracked at a time within the station 41. The mechanism for cracking nuts includes anvil means generally denoted 66 and hammer means generally denoted 67. The anvil means comprises a plurality of separate anvil structures 68, each of which is substantially identical, there being four in number in the specific machine being considered. As shown best in FIGS. 3, 4 and 9, each of the anvil structures comprises a generally cylindrical anvil 69 equipped at one end thereof with a serrated nut-engaging head 70 and supported for axial displacements by spaced apart bearings 71 and 72 carried by a mounting plate 73 bolted or otherwise fixedly secured to a transversely extending plate 74 forming a part of the frame structure 15 of the machine.

Each anvil 69 is displaceable between an outer retracted position shown in FIGS. 3 and 9 and an inner operative position illustrated in FIG. 7; and in being movable between such inner and outer positions, the head 70 of the anvil 69 passes through an opening provided therefor in a longitudinally disposed plate or guide 75 extending along the chain 26b of the conveyor apparatus 24. Inward displacements of the anvil .69 into the operative position thereof shown in FIG. 7 are imparted thereto by motor means in the form of fluid-actuated piston and cylinder structure 76 having a reciprocable piston rod 77 attached to the anvil 69 so as to reciprocate the same. The piston-cylinder structure 76 may be hydraulically or pneumatically energized, and in the form shown is a one-way device in which (upon admission of fluid to the cylinder) the piston thereof is displaced in a direction to move the rod 77 and anvil 69 outwardly into the extended position shown in FIG. 7.

The piston-cylinder structure 76 is so energized whenever a control valve is actuated by engagement of a lever 78 thereof with a cam-controlled actuator 79 in the form of a bell crank supported intermediate its ends by a shaft 80 for angular displacements about the axis thereof. The actuator 79 has an upwardly extending arm 81 in operative engagement with the lever 78 and a laterally extendingcrank arm 82 equipped with a cam follower 83 ridingly engaging a cam 84 that is keyed or otherwise secured to a cam shaft 85 so as to rotate therewith. Evidently, as the cam shaft 85 rotates, the cam 84 cyclically displaces the actuator 79 between the outer position shown in which the valve is closed and an innner position in which the actuator 79 is displaced in a clockwise direction (as viewed in FIG. 9) to displace the lever 78 inwardly and thereby cause the piston-cylinder structure 76 to be energized to displace the anvil structure 69 into the extended position thereof.

Actuating fluid is supplied to the valve and motor means through an inlet conduit 86 connected (as shown in FIG. 1) to a manifold 87 which communicates through a valve-equipped supply conduit 88 with a supply or surge tank 89 adapted to be connected to a compressor or other source of pressurized fluid through an inlet conduit 90. Therefore, when the valve is opened by appropriate inward displacement of the lever 78 through action of the actuator 79 and cam 84, the pistoncylinder structure 76 is energized to displace the anvil 69 out wardly; and as the cam 84 continues to rotate until the actuator 79 and lever 78 are in the position shown, the pistoncylinder structure 76 is exhausted through the port or conduit 91 to condition the motor meansfor return displacement of the anvil 69 into the retracted position-thereof shown in FIG. 9

Such return movement of the anvil is enforced thereon by means of a cam 92 mounted upon the cam shaft 85 so as to rotate therewith in enforced synchronism with the cam 84, and which cam 92 is ridingly engaged by the cam follower 93 of a cam arm 94 supported for angular displacements by a shaft 95. The cam arm 94 hm an end portion 96 defining a tongue that extends upwardly and into a notch or. recess 97 formed in the anvil 69. The cam arm 94 and follower 93 thereof are so related to the cam 92 that that the anvil 69 is free to be displaced outwardly into its operative position whenever the ,lever 78 opens the valve to energize the pistoncylinder structure 76; and subsequent to the piston-cylinder structure being deenergized by return of the lever 78 into the closed position shown by further rotation of the cam 84, the cam 92 causes the cam arm 94 to. rotate in a' clockwise direction into the position shown in FIG. 9 which causes the anvil 69 and piston rod 77 connected therewith to be returned to the retracted position illustrated.

Any slight differences that may be encountered in the size of the nuts 23 advanced into position by the conveyor apparatus 24 in front of the respective anvils 69 are accommodated by the respective piston-cylinder structures 76 which are operative, when energized, to displace the associated an vils 69 inwardly and into engagement with the nuts aligned therewith, and which nuts are concurrently engaged and held againstdisplacement by the hammer means 67, as will be described hereinafter. That is to say, within the limits of maximum inward displacement defined by each piston-cylinder structure 76 and the rod 77 associated therewith, the anvil 69 is moved inwardly until the resistance to further movement resulting from immobility of the nut 23 terminates such movement. The magnitude of the resistive force effective to constrain the rod 77 against further movement is of predetermined value, and is established for any given piston size by the pressure of the fluid supplied thereto-the maximum value of which may be established for each piston-cylinder structure by conventional pressure relief means associated therewith. Thus, for a nut of somewhat larger size, the resistive force established thereby will become operative against the anvil 69 to terminate its inward movement sooner than the corresponding resistive force applied by a out of smaller size which, in the case of a smaller nut, will therefore permit the anvil associated therewith to move inwardly to a greater extent.

The hammer means 67 comprises a plurality of hammer structures 98 each of which is substantially identical, there being four in number in the specific machine being considered. As shown best in FIGS. 3,. 4, 7 and 8, each of the hammer structures 98 comprises a generally cylindrical hammer 99 equipped at one end thereof with a serrated head 100 and supported for axial displacements by spaced apart bearings 101 and 102 carried by a mounting plate 103 bolted or otherwise fixedly secured to a transversely extending plate 104 forming a part of the frame structure of the machine. Each hammer 99 is displaceable between an outer retracted position shown in FIG. 3 and an inner operative position illustrated in FIG. 7; and in being movable between such inner and outer positions, the head 100 of the hammer 99 passes through an opening provided therefor in a longitudinally disposed plate or guide 105 extending along the chain 26a of the conveyor apparatus 24.

Inward displacements into the operative position shown in FIG. 7 are imparted to the hammer 99 by a gripper or holder device 106 of U-shaped construction, as shown in FIG. 8, which has spaced part apart legs equipped with collars 107 and 108 supported for pivotal movement by symmetrical,

' cylindrical bearings upon a shaft 109. The collar 108 has a cam arm 110 extending downwardly therefrom which is equipped with a rotatable cam follower 111 that ridingly engages a cam 112 pinned or otherwise constrained upon a cam shaft 113 so as to be rotatably driven thereby. The cam 112 is configurated so as to displace the grip-per device 106 inwardly between the full line position thereof shown in FIG. 7 and an outer position shown by broken lines in such FIG. Upon being displaced by the cam 112 into its inward position, the upper arcuate end portion of the holder device 106 engages the enlarged hammer surface or outer end portion 114 of the hammer 99 to push the same inwardly into an inner position in which it is in engagement with a nut 23, and which inner position thereof is somewhat less than the inner position of the hammer 99 shown in FIG. 7.

The holder 106 displaces the hammer 99 inwardly to bring the same into engagement with one end portion of a nut 23 at substantially the same time that the actuation of the pistoncylinder structure 76 displaces the associated anvil 69 inwardly to engage such nut at the opposite end thereof, whereupon the nut is then held in a predetermined position between the heads 70 and 100 respectively provided by the anvil 69 and hammer 99. Subsequent to the nut being so gripped and held in such position, a cracker device 115 is operative to deliver sufficient force to a hammer surface 114 on the hammer 99 to thrust the same inwardly into the position shown in FIG. 7, which inward displacement causes the shell of the nut 23 engaged by the hammer head 100 to crack or shatter. The cracker device 115 is somewhat in the form of a bell crank supported intermediate the ends thereof (upon an eccentric bearing 115a, the purpose of which will be described subsequently) by the shaft 109 for pivotal displacements with respect thereto.

The cracker device 115 has an arm 116 extending downwardly from the shaft 109, and at its lower end the arm is equipped with a rotatable cam follower 117 that ridingly engages a cam 118 pinned or secured to the cam shaft 113 so as to rotate therewith. The cam 118, as shown in FIG. 7, has a relatively sharp rise and fall which causes the cracker device 1 15 to be displaced inwardly in a clockwise direction (FIG. 7)

at a sufficiently high acceleration to effectively impact the I hammer surface 114 of the hammer 99 and therefore cause the same to deliver impact force to a nut 23 to crack the same. In order to accomplish this impact-delivering function, the

device 115 has an arm 119 extending upwardly above the arm 122 having an end portion 124 defining a tongue that extends upwardly and into a notch or recess 125 formed in the hammer 99. Observing the configuration of the cams 112 and 118, it will be evident that the cam 112 (which rotates in a clockwise direction as viewed in FIG. 7) enables the holder device 106 to return in a counterclockwise direction to its inoperative retracted position remote from the hammer 99 at about the same time that the cam 118 enables the cracker device 115 to return in a counterclockwise direction (as seen in FIG. 7) to its inoperative retracted position. Accordingly, the hammer 99 is then free of restraint and can be returned to its retracted position by the arm 122 and spring 121 bearing thereagainst.

Referring to FIG. 3, an adjustment is provided for changing the throw or extent of inward angular displacement of the cracker devices 1 15, and such adjustment comprises a plate or flange-equipped collar 126 located adjacent the vertically disposed and transversely extending frame element 127 forming a part of the frame structure of the machine and angularly displaceable with respect to the frame element within the limits defined by an arcuate slot 128 formed in the collar and a fastener pin 129 in the form of a cap screw extending through such slot and threaded into the frame element 127, thereby releasably securing the collar 126 in any position of adjustment thereof. The collar is keyed or otherwise secured to the shaft 109, and it has an arm or handle 130 extending outwardly from the side of the machine so as to facilitate manual manipulation of the adjustment upon release of the fastener 129. Angular displacement of the collar 126 causes the shaft 109 to be displaced therewith which changes the throw of the cracker devices 115 because each device is pivotally supported upon one of the bearings 115a which are keyed to the shaft 109 so as to be displaced therewith and in being eccentrically related thereto, shift the pivot axes of the cracker devices. The extent of such adjustment is very slight, as is the corresponding change in the amount of displacement or throw of the cracker devices 115.

As shown in FIG. 10, the head 70 of each anvil 69 is removable so that it can be replaced when necessary; and in this respect, each such head is provided with a stub shaft 131 slidable inwardly into a passage 132 provided within the anvil 69 and located in position therewithin by a set screw 133. The head 100 of each hammer 99 is similarly removable and, therefore, the structure shown in FIG. 10 may be taken to apply equally to the anvil and hammer structures.

Further as concerns the hammer and anvil structures, by referring to FIG. 4 it will be seen that the cam shaft 85 is continuously driven by the main drive shaft 50 by right-angle bevel gears 134 and 135, and the cam shaft 113 is correspondingly driven via bevel gears 136 and 137. It will be understood that the usual spring devices are employed to resiliently bias the various cam arms and followers toward engagement with the respectively associated cams, and that any differences in gear sizes are used to obtain the angular velocities and rates of movement necessary to time the various functions of the machine.

OPERATION In operation of the machine, nuts 23 are placed within the container 21, fluid pressure is supplied to the tank 89 and the various valves associated therewith are opened to supply fluid under pressure to the manifold 87, and the motor 47 is energized so as to drive the conveyor apparatus 24 and effect operational displacements of the anvil means 66 and hammer means 67. Since the conveyor apparatus 24, anvil means 66 and hammer means 67 are driven in mechanically enforced synchronism by the motor 47, it will be evident that the operation of the anvil and hammer means is timed with the conveyor apparatus 24 so that the anvil and hammer means function to crack nuts displaced into the cracking station 41 after the conveyor has displaced a group of four nuts thereinto.

After a group of nuts has been cracked and the anvil and hammer means returned to their retracted positions, the conveyor apparatus 24 is again actuated to displace such four cracked nuts from the cracking station 41 and advance the next four successive nuts thereinto. The cracked nuts including the shells and kernels are discharged into a suitable container (not shown) as the conveyor structure 24 traverses the sprockets 29, and a suitable receptacle may be placed beneath the cracking station 41 to collect any nut fragments that may sift downwardly therefrom. As shown in FIG. 7, the plates 75 and tend to confine the nut fragments and particles therebetween as the nuts are cracked by operation of the anvil and hammer means.

As the conveyor apparatus 24 is cyclically displaced through a distance equivalent to a sequence of four successive nuts being discharged from the cracking station and another four nuts being advanced thereinto, nuts 23 within the container 21 are engaged by successive flights 37 which seat such nuts within the concavities 38 thereof and thereby carry the nuts upwardly to the horizontal branch of the conveyor structure defined between the sprockets 28 and 29 thereof. As each flight 37 traverses the arcuate path defined by the sprockets 28, the nut 23 carried by the flight drops therefrom into the pocket 31 defined by the adjacent rollers 30 located between successive flights. Such rollers as they traverse the support bar 42 tend to align the nuts 23 so that the maximum dimension thereof is transversely disposed with respect to the conveyor apparatus.

As explained heretofore, the conveyor apparatus 24 is intermittently actuated so as to be cyclically displaced through predetermined distances respectively corresponding generally to the longitudinal length of the cracking station 41 because of the function of the crank plate 54, crank 55, rod 56, arm 57, disc 58 and associated one-way drive structure which imparts unidirectional motion to the shaft 60 and conveyor apparatus as the arm 57 is cyclically reciprocated in opposite angular directions as the disc 54 rotates continuously in the direction of the arrow, as viewed in FIG. 2. During the 180 displacement of the disc 54 throughout which the conveyor structure 24 is inoperative or stationary, the four anvils 69 comprised by the anvil means 66 and the four hammers 99 comprised by the hammer means 67 are actuated so as to be displaced inwardly and grip the nuts respectively aligned with the four paired anvil and hammer structures, and then to crack such nuts whereupon the hammer and anvil structures are then retracted. Such structures remain inoperative as the disc 54 rotates through the next successive 180 during which the conveyor structure 24 is caused to displace the four nuts from the cracking station and to advance the next group of four nuts thereinto.

As explained hereinbefore, each hammer 99 traverses essentially a two-position inward displacement the first of which is enforced thereon by the associated holder device 106 and is effective with the anvil structure aligned therewith to grip or hold a nut located therebetween, and the second position of which is enforced thereon by the impact force delivered thereto by the associated cracking device which further displaces the hammer 99 inwardly and thereby effects a cracking or fragmentation of the nutshell since the nut is then constrained against movement by the aligned anvil structure.

While in the foregoing specification an embodiment of the invention has been set forth in considerable detail for purposes of making a complete disclosure thereof, it will be apparent to those skilled in the art that numerous changes may be made in such details without departing from the spirit and principles of the invention.

I claim:

1. In a machine for cracking the shells of nuts and the like to provide access to the kernels therewithin, cracking mechanism including anvil structure having an anvil element selectively movable between an outer retracted position and an inner extended position for engagement with a nut aligned therewith and further including hammer structure having a hammer element selectively movable between an outer retracted position and an inner extended position for engagement with such nut and being operative to impart a cracking force to the shell thereof, and drive mechanism for selectively displacing said anvil and hammer elements between the inner and outer positions thereof; said hammer structure comprising a gripper element operative to displace said hammer element inwardly to a mechanically-enforced predetermined gripping position in timed relation with the inward movement of said anvil element so as to engage and grip therewith a nut positioned therebetween, and also comprising a cracking device operative to further displace said hammer element inwardly toward the associated anvil structure into a mechanically-enforced predetermined cracking position to impart a force to such nut sufficient in magnitude to crack the shell thereof; and said anvil structure providing said anvil element with a resistive force against such nut of substantially uniform magnitude throughout the range of movement of said hammer element from the gripping position into the cracking position thereof.

2. The machine of claim 1 in which said drive mechanism includes both a gripper cam arranged with said gripper element for controlling the operation thereof and a cracking cam arranged with said cracking device for controlling its opera tion, said gripper and cracking cams being related with respect to each other so as to cause said cracking device to displace said hammer element inwardly subsequent to the inward displacement imparted thereto by said gripper element, and said cracking cam having a relatively sharp rise so as to rapidly accelerate said cracking device toward and into engagement with said hammer element to impart an impact-type forc thereto. 5

3. The machine of claim 1 in which said drive mechanism includes fluid motor means for displacing said anvil element inwardly.

4. The machine of claim 3 in which said anvil structure comprises valve structure adapted to be connected to a source of pressurized fluid and being connected with said fluid motor means so as to deliver such fluid thereto, said valve structure being equipped with an actuator selectively movable between positions opening and closing said valve to control the supply of fluid therefrom to said fluid motor means and thereby control energization thereof, and cam means forming apart of said drive mechanism and arranged with said actuator for moving the same to control operation of said motor means.

5. In a machine for cracking the shells of nuts and the like to provide access to the kernels therewithin, a container defining a compartment adapted to receive'a mass of such nuts therein; conveyor apparatus for transporting nuts from said container to a cracking station and for advancing such nuts in single-file succession therethrough; cracking mechanism at such station for cracking the shells of nuts advanced thereinto including anvil structure having an anvil element selectively movable between an outer retracted position and an inner extended position for engagement with such nut and further including hammer structure having a hammer element selectively movable between an outer retracted position and an inner extended position for engagement with such nut and being operative to impart a cracking force to the shell thereof; and drive mechanism for operating said conveyor apparatus, anvil structure and hammer structure in timed relation so as to cause said structures to engage and crack each nut advanced by said conveyor apparatus into the cracking station; said hammer struc ture comprising a gripper element operative to displace said hammer element inwardly to a mechanically-enforced predetermined gripping position in timed relation with the inward movement of said anvil element so as to engage and grip therewith a nut positioned therebetween, and also comprising a cracking device operative to further displace said hammer element inwardly toward the associated anvil structure into a mechanically-enforced predetermined cracking position to impart a force to such nut sufficient in magnitude to crack the shell thereof; and said anvil structure providing said anvil element with a resistive force against such nut of substantially uniform magnitude throughout the range of movement of said hammer element from the gripping position into the cracking position thereof.

6. The machine of claim 5 in which said drive mechanism includes both a gripper cam arranged with said gripper ele ment for controlling the operation thereof and a cracking cam arranged with said cracking device for controlling its operation, said gripper and cracking cams being related with respect to each other so as to cause said cracking device to displace said hammer element inwardly subsequent to the inward displacement imparted thereto by said gripper element, and said cracking cam having a relatively sharp rise so as to rapidly accelerate said cracking device toward and into engagement with said hammer element to impart an impact-type force thereto, and to which said drive mechanism includes fluid motor means for displacing said anvil element inwardly. 

1. In a machine for cracking the shells of nuts and the like to provide access to the kernels therewithin, cracking mechanism including anvil structure having an anvil element selectively movable between an outer retracted position and an inner extended position for engagement with a nut aligned therewith and further including hammer structure having a hammer element selectively movable between an outer retracted position and an inner extended position for engagement with such nut and being operative to impart a cracking force to the shell thereof, and drive mechanism for selectively displacing said anvil and hammer elements between the inner and outer positions thereof; said hammer structure comprising a gripper element operative to displace said hammer element inwardly to a mechanically-enforced predetermined gripping position in timed relation with the inward movement of said anvil element so as to engaGe and grip therewith a nut positioned therebetween, and also comprising a cracking device operative to further displace said hammer element inwardly toward the associated anvil structure into a mechanically-enforced predetermined cracking position to impart a force to such nut sufficient in magnitude to crack the shell thereof; and said anvil structure providing said anvil element with a resistive force against such nut of substantially uniform magnitude throughout the range of movement of said hammer element from the gripping position into the cracking position thereof.
 2. The machine of claim 1 in which said drive mechanism includes both a gripper cam arranged with said gripper element for controlling the operation thereof and a cracking cam arranged with said cracking device for controlling its operation, said gripper and cracking cams being related with respect to each other so as to cause said cracking device to displace said hammer element inwardly subsequent to the inward displacement imparted thereto by said gripper element, and said cracking cam having a relatively sharp rise so as to rapidly accelerate said cracking device toward and into engagement with said hammer element to impart an impact-type force thereto.
 3. The machine of claim 1 in which said drive mechanism includes fluid motor means for displacing said anvil element inwardly.
 4. The machine of claim 3 in which said anvil structure comprises valve structure adapted to be connected to a source of pressurized fluid and being connected with said fluid motor means so as to deliver such fluid thereto, said valve structure being equipped with an actuator selectively movable between positions opening and closing said valve to control the supply of fluid therefrom to said fluid motor means and thereby control energization thereof, and cam means forming a part of said drive mechanism and arranged with said actuator for moving the same to control operation of said motor means.
 5. In a machine for cracking the shells of nuts and the like to provide access to the kernels therewithin, a container defining a compartment adapted to receive a mass of such nuts therein; conveyor apparatus for transporting nuts from said container to a cracking station and for advancing such nuts in single-file succession therethrough; cracking mechanism at such station for cracking the shells of nuts advanced thereinto including anvil structure having an anvil element selectively movable between an outer retracted position and an inner extended position for engagement with such nut and further including hammer structure having a hammer element selectively movable between an outer retracted position and an inner extended position for engagement with such nut and being operative to impart a cracking force to the shell thereof; and drive mechanism for operating said conveyor apparatus, anvil structure and hammer structure in timed relation so as to cause said structures to engage and crack each nut advanced by said conveyor apparatus into the cracking station; said hammer structure comprising a gripper element operative to displace said hammer element inwardly to a mechanically-enforced predetermined gripping position in timed relation with the inward movement of said anvil element so as to engage and grip therewith a nut positioned therebetween, and also comprising a cracking device operative to further displace said hammer element inwardly toward the associated anvil structure into a mechanically-enforced predetermined cracking position to impart a force to such nut sufficient in magnitude to crack the shell thereof; and said anvil structure providing said anvil element with a resistive force against such nut of substantially uniform magnitude throughout the range of movement of said hammer element from the gripping position into the cracking position thereof.
 6. The machine of claim 5 in which said drive mechanism includes both a gripper cam arranged with said gripper element for controlling the operation thereof and a cracking Cam arranged with said cracking device for controlling its operation, said gripper and cracking cams being related with respect to each other so as to cause said cracking device to displace said hammer element inwardly subsequent to the inward displacement imparted thereto by said gripper element, and said cracking cam having a relatively sharp rise so as to rapidly accelerate said cracking device toward and into engagement with said hammer element to impart an impact-type force thereto, and to which said drive mechanism includes fluid motor means for displacing said anvil element inwardly. 